CN111765194B - Hydraulic damper assembly - Google Patents
Hydraulic damper assembly Download PDFInfo
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- CN111765194B CN111765194B CN202010584792.7A CN202010584792A CN111765194B CN 111765194 B CN111765194 B CN 111765194B CN 202010584792 A CN202010584792 A CN 202010584792A CN 111765194 B CN111765194 B CN 111765194B
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- insert
- main
- damper assembly
- diameter
- hydraulic damper
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
- F16F9/49—Stops limiting fluid passage, e.g. hydraulic stops or elastomeric elements inside the cylinder which contribute to changes in fluid damping
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
- B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
- B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
- B60G13/08—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type hydraulic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/30—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium with solid or semi-solid material, e.g. pasty masses, as damping medium
- F16F9/303—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium with solid or semi-solid material, e.g. pasty masses, as damping medium the damper being of the telescopic type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3271—Assembly or repair
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/346—Throttling passages in the form of slots arranged in cylinder walls
- F16F9/3465—Slots having a variable section along their length
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/20—Type of damper
- B60G2202/24—Fluid damper
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2222/00—Special physical effects, e.g. nature of damping effects
- F16F2222/10—Adhesion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2222/00—Special physical effects, e.g. nature of damping effects
- F16F2222/12—Fluid damping
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2226/00—Manufacturing; Treatments
- F16F2226/04—Assembly or fixing methods; methods to form or fashion parts
- F16F2226/045—Press-fitting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/001—Specific functional characteristics in numerical form or in the form of equations
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2234/00—Shape
- F16F2234/02—Shape cylindrical
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
- F16F9/185—Bitubular units
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Abstract
The invention provides a hydraulic damper assembly. A hydraulic damper assembly includes a main tube defining a fluid chamber. An outer tube extends around the main tube defining a compensation chamber between the main tube and the outer tube. A main piston located in the main tube divides the fluid chamber into a compression chamber and a rebound chamber. The piston rod is coupled to the main piston. A base valve located in the compression chamber is coupled to the main pipe. A hydraulic compression stop located in the compression chamber includes an additional piston, an insert, and a fixed member. The additional piston is coupled to the main piston. An insert located in the compression chamber is coupled to the base valve. The insert has a main section and a tip section. The outer diameter of the end section is smaller than the outer diameter of the main section.
Description
Technical Field
The present invention generally relates to a hydraulic damper assembly for a vehicle.
Background
Hydraulic damper assemblies including a hydraulic compression stop ("HCS") are known in the art for generating an additional damping force over a predetermined section of the piston rod stroke during a compression stroke. One such hydraulic damper assembly is disclosed in PCT patent publication WO 2019167006.
In known solutions, the insert of the HCS may be press-fitted onto the fixation member by pressing a simple tubular end section of the insert with a constant wall thickness onto the head of the fixation member. In order to obtain the tightness required for a press-fit connection, a relatively high degree of connection interference (tightness) must be achieved, which may damage the head during the press-fit process. Furthermore, the presence of the insert inside the compression chamber may affect the flow of the working fluid through the compression chamber.
Disclosure of Invention
The present invention provides a hydraulic damper assembly that minimizes the effect of the HCS on the flow of working fluid through the compression chambers of the hydraulic damper assembly. The present invention also provides a hydraulic damper assembly including an HCS having an improved press-fit connection between the insert and the head, thereby creating minimal restriction to the flow of working fluid through the base valve.
One aspect of the present invention provides a hydraulic damper assembly. The hydraulic damper assembly includes a main tube extending along a central axis defining a fluid chamber for containing a working fluid. An outer tube extends around the main tube defining a compensation chamber extending between the main tube and the outer tube. A main piston is located in the main tube, dividing the fluid chamber into a compression chamber and a rebound chamber. A piston rod extends into the main tube and is coupled to the main piston for moving the main piston between a compression stroke and a rebound stroke. A base valve is located in the compression chamber and is coupled to the main tube for controlling working fluid flow between the compression chamber and the compensation chamber. A hydraulic compression stop is located in the compression chamber for providing an additional damping force during the compression stroke. The hydraulic compression stop includes an additional piston and an insert. The additional piston is coupled to the master piston for movement with the master piston between the compression stroke and the rebound stroke. The insert is located in the compression chamber, coupled to the base valve. The insert has a main section and a tip section. The end section is located adjacent to the fixation member. The main section is in fluid communication with the tip section. The end section has an outer diameter smaller than an outer diameter of the main section.
Another aspect of the present invention provides a hydraulic damper assembly. The hydraulic damper assembly includes a main tube extending along a central axis defining a fluid chamber for containing a working fluid. An outer tube extends around the main tube defining a compensation chamber extending between the main tube and the outer tube. A main piston is located in the main tube, dividing the fluid chamber into a compression chamber and a rebound chamber. A piston rod extends into the main tube and is coupled to the main piston for moving the main piston between a compression stroke and a rebound stroke. A base valve is located in the compression chamber and is coupled to the main tube for controlling working fluid flow between the compression chamber and the compensation chamber. A hydraulic compression stop is located in the compression chamber for providing an additional damping force during the compression stroke. The hydraulic compression stop includes an additional piston, an insert, and a stationary member. The additional piston is coupled to the master piston for movement with the master piston between the compression stroke and the rebound stroke. The securing member is located between the main pipe and the foot valve for coupling the foot valve to the main pipe. The insert is located in the compression chamber, coupled to the fixation member. The stationary member includes a head portion that extends outwardly from the stationary member and along the central axis toward the master piston. The tip section of the insert includes an inner flange extending radially inward toward the central axis. The inner flange defines a mounting opening for receiving the head to establish a press-fit engagement.
Drawings
Other advantages of the present invention will be readily appreciated, as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:
FIG. 1 is a partial view of a vehicle including a hydraulic damper assembly constructed in accordance with an embodiment of the present invention;
FIG. 2 is a cross-sectional view of a hydraulic damper assembly constructed in accordance with an embodiment of the present invention;
FIG. 3 is a perspective view of the base valve and a cross-sectional perspective view of the insert press fit onto the stationary member of the hydraulic compression stop;
FIG. 4 is a perspective view of the base valve including an insert press fit onto a stationary member of the hydraulic compression stop;
FIG. 5 is a cross-sectional view of an insert constructed in accordance with an embodiment of the invention; and
fig. 6a to 6f illustrate a process of manufacturing an insert.
Detailed Description
Referring to the drawings, wherein like reference numbers refer to corresponding parts throughout the several views, fig. 1 illustrates a hydraulic damper assembly 1 constructed in accordance with an embodiment of the present invention, the hydraulic damper assembly 1 being coupled to a vehicle chassis 101. Hydraulic damper assembly 1 may be coupled to vehicle chassis 101 using a top mount 102 and a plurality of screws 103, wherein the plurality of screws 103 are disposed along a periphery of an upper surface of top mount 102. Top mount 102 is coupled to coil spring 104 and piston rod 5 of hydraulic damper assembly 1. The outer tube 2 of the hydraulic damper assembly 1 may be coupled to a knuckle 105 supporting a wheel 106.
Fig. 2 illustrates a double tube damper 1 (also referred to as a hydraulic damper assembly 1) constructed in accordance with an embodiment of the present invention. The hydraulic damper assembly 1 comprises an outer tube 2 and a main tube 3. The main tube 3 extends along a central axis a and defines fluid chambers 11, 12 for containing a viscous working fluid. The outer tube 2, which is radially spaced from the main tube 3, extends along the main tube and defines a compensation chamber 13 extending between the main tube 3 and the outer tube 2. A main piston 4 located in the main pipe 3 divides the fluid chambers 11, 12 into a compression chamber 12 and a rebound chamber 11. The piston rod 5 extends into the main tube 3 through a piston rod guide 6. A piston rod guide 6 is coupled to one end of the main tube 3, wherein one end of the piston rod 5 in the fluid chambers 11, 12 is coupled to the main piston 4 and the other end of the piston rod 5 extends outside the hydraulic damper assembly 1. The piston rod 5 moves the main piston 4 between a compression stroke and a rebound stroke. During the compression stroke, the piston rod 5 and the main piston 4 move axially away from the piston rod guide 6 in the fluid chambers 11, 12. During a rebound stroke, the piston rod 5 and the main piston 4 move axially in the fluid chambers 11, 12 towards the piston rod guide 6.
The hydraulic damper assembly 1 includes a foot valve 7 coupled at the other end of the main pipe 3. The main piston 4 is in sliding engagement with the inner surface of the main pipe 3, dividing the fluid chambers 11, 12 of the main pipe 3 into a rebound chamber 11 and a compression chamber 12. A rebound chamber 11 extends between the main piston 4 and the piston rod guide 6. A compression chamber 12 extends between the main piston 4 and the base valve 7, wherein the base valve 7 restricts the working fluid flow between the compression chamber 12 and the compensation chamber 13.
According to an embodiment of the invention, the main piston 4 may be provided with a rebound valve 41 and a compression valve 42. Rebound valve 41 and compression valve 42 may comprise a stack of deflectable or floating discs, optionally biased by springs, for controlling the flow of working fluid between rebound chamber 11 and compression chamber 12 through main piston 4 in response to axial movement of main piston 4 along central axis a. Additionally, the base valve 7 may be provided with a rebound valve 71 and a compression valve 72 for controlling the flow of working fluid passing between the additional compensation chamber 13 and the compression chamber 12 during a rebound stroke and a compression stroke, respectively, of the hydraulic damper assembly 1. It should be appreciated that rebound valves 41 and compression valves 42 of main piston 4 and rebound valves 71 and compression valves 72 of base valve 7 may provide design parameters that may be used to shape the desired passive characteristics of hydraulic damper assembly 1.
The hydraulic damper assembly 1 includes a hydraulic compression stop 8 in the compression chamber for providing an additional damping force at the end of the compression stroke to avoid sudden stopping of the main piston 4. As best shown in fig. 3-5, the hydraulic compression stop 8 includes an insert 81, a fixed member 82, and an additional piston 83.
As best shown in fig. 5, the insert 81 has a generally tubular shape and defines an inner chamber 813 extending along the central axis a. The inner portion 813 is in fluid communication with the compression chamber 12 for receiving the additional piston 83 during a compression stroke. The inner chamber 813 extends between an entry point and an end point. Near the entry point of the inner chamber 813, the inner surface of the insert 81 defines a plurality of grooves 814, the plurality of grooves 814 extending along the inner surface of the insert 81 towards the terminus. According to an embodiment of the present invention, the plurality of grooves 814 comprises six grooves equiangularly arranged around the central axis and spaced apart from each other for allowing the working fluid to exit the inner chamber 813 during the compression stroke. As the groove 814 extends along the central axis a, the depth of the groove 814 also decreases. Therefore, as the depth of the groove 814 decreases, the damping force increases. In cross-sectional view, the inner surface of the insert 81 has a tapered section 811 near the entry point followed by a cylindrical section 812. According to an embodiment of the invention, the tapered section 811 may comprise two tapered sub-sections 811a, 811b having different angles of inclination. It will be appreciated that the tapered section 811 assists and guides the additional piston 83 into the inner chamber 813. In addition, it should be appreciated that such shaping, in conjunction with the groove 814, provides a smooth build of damping force.
According to an embodiment of the invention, the insert 81 has an outer diameter Dm, Dd which is smaller than the inner diameter of the main tube 3. Thus, the insert 81 and the main tube 3 define an axial annular channel between the outer surface of the insert 81 and the inner surface of the main tube 3. The axial annular channel 31 allows the working fluid to flow around the insert 81 between the compression chamber 12 and the compensation chamber 13 through the base valve 7 during the compression stroke and the rebound stroke.
According to embodiments of the present invention, the inner diameter Dv of the inner chamber 813 may be constant along approximately the entire length L of the inner chamber 813, except for the tapered section 811. At the tapered section 811, the inner diameter gradually increases toward the entry point of the inner chamber 813.
According to an embodiment of the present invention, insert 81 may include a main section 815 and a tip section 816. The tip section 816 is located near the foot valve 7. The main section 815 is in fluid communication with the tip section 816. The main section has an outer diameter Dm and a length Lm extending from the entry point of the inner chamber 813. The tip section 816 has an outer diameter Dd extending from the end of the inner chamber 813, wherein the outer diameter Dd of the tip section 816 is smaller than the outer diameter Dm of the main section 815.
The fixing member 82 is located between the main pipe 3 and the foot valve 7 for coupling the foot valve 7 to the main pipe 3. According to an embodiment of the present invention, the fixing member 82 may be made of sintered steel and may have a tensile strength (Rm) greater than or equal to 300Mpa, a yield strength (Re) greater than or equal to 250Mpa, and a rockwell B hardness of at least 51 HRB. The fixing member 82 may include a cylindrical body 821. The head 822 extends outwardly from the fixed member 82 and along the central axis a toward the master piston 4. The fixed member 82 defines a cavity located in the compensation chamber 13 and in fluid communication with the compensation chamber 13. The cavity has an inner cylindrical surface 823 for accommodating the foot valve 7, wherein the foot valve 7 is coupled to the fixation member 82 by press fitting against the inner cylindrical surface 823. Cylindrical body 821 has an outer cylindrical surface 824 extending about cylindrical body 821, with outer cylindrical surface 824 being easily press fit against main tube 3 to secure fixation member 82 to main tube 3. The stationary member 82 defines a plurality of axial passages 825, the plurality of axial passages 825 extending through the stationary member 82, fluid communication between the compression chamber 12 and the compensation chamber 13 being achieved through the base valve 7 during the compression stroke and the rebound stroke. According to an embodiment of the present invention, the plurality of axial passages 825 includes eight axial passages 825, the eight axial passages 825 being equiangularly spaced from each other about the central axis a and extending through the fixation member 82.
At the end of the inner chamber 813, the insert 81 includes an inner flange 817 extending radially inward toward the central axis a. Inner flange 817 defines a mounting opening 8171 in which insert 81 is sealingly press-fit against head 822 of securing member 82, such as press-fitting insert 81 onto head 822 of securing member 82. Subsequently, the foot valve 7 is press-fitted into the inner cylindrical surface 823 of the cavity of the fixing member 82. Then, the outer cylindrical surface 824 of the fixing member 82 is press-fitted into the main tube 3. It should be understood that, according to an embodiment of the present invention, instead of being coupled to the fixing member 82, the insert 81 may be directly coupled to the foot valve 7 without any direct connection with the main pipe 3. Additionally, in accordance with embodiments of the present invention, instead of securing member 82, head 822 may extend outwardly from base valve 7 for receiving inner flange 817 of insert 81.
According to an embodiment of the present invention, the diameter Df of the mounting opening 8171 is smaller than the diameter Dh of the head 822 of the fixation member 82. Specifically, the difference between the diameter Df of the mounting opening 8171 and the diameter Dh of the head 822 may be in the range of 0.01mm to 0.5 mm. In addition, the height Hf of the inner flange 817 is greater than the height Hh of the head 822, wherein the ratio of the height Hf of the inner flange 817 to the height Hh of the head 822 (Hf: Hh) may be less than 2. Advantageously, increasing the height Hf of the inner flange 817 relative to the height Hh of the head 822 can provide additional sealing between the inner flange 817 and the head 822. Between the main section 815 and the end section 816, an intermediate section 818 may be formed, wherein the outer diameter of the end section 816 gradually increases towards the main section 815.
Further, upon assembly, the inner flange 817 provides additional press fit force against the head 822, thereby creating additional sealing force. During the compression stroke, additional fluid pressure is generated by the additional piston 83 against the inner surface F of the inner flange 817. The additional sealing force improves the seal between the outer front surface of the inner flange 817 and the cylindrical body 821 of the fixing member 82. Thus, to achieve the desired seal between the insert 81 and the securing member 82, a relatively low degree of interference (tightness) may be employed, thereby greatly reducing the risk of damaging the head 822 during handling of the press-fit insert 81.
In order to obtain a positive influence of the inner flange 817 on the optimization of the tightness between the insert 81 and the head 822, and a possible reduction of the interference (tightness), the diameter Df of the mounting opening 8171 may, according to an embodiment of the invention, satisfy the following equation:
where Df is the diameter of the mounting opening 8171;
dv is the inner diameter of the insert 81;
dm is the outer diameter of the main section 815 of the insert 81;
a is 1.1 to 1.6; and is
b is 1.0 to 1.5, wherein b Dv < a Dm.
According to an embodiment of the present invention, the diameter Df of the mounting opening 8171 may satisfy the following equation:
where Df is the diameter of the mounting opening 8171;
dv is the inner diameter of the insert 81;
dm is the outer diameter of the main section 815 of the insert 81;
a is 1.1 to 1.6; and is
b is 1.0 to 1.5, wherein b Dv < a Dm.
According to an embodiment of the present invention, the inner diameter Dv of the insert 81 may satisfy the following formula:
where Dv is the inner diameter of the insert 81;
dd is the outer diameter of the tip segment 816;
dm is the outer diameter of the main section 815 of the insert 81;
a is 1.1 to 1.6; and is
b is 1.0 to 1.5, wherein b Dv < a Dm.
According to an embodiment of the present invention, the inner diameter Dv of the insert 81 may have a maximum value defined by:
where Dvmax is the maximum value of the inner diameter of the insert 81;
dd is the outer diameter of the tip segment 816;
dm is the outer diameter of the main section 815 of the insert 81;
a is 1.1 to 1.6; and is
b is 1.0 to 1.5, wherein b Dv < a Dm.
According to an embodiment of the present invention, the diameter Df of the mounting opening 8171 may have a minimum value defined by:
wherein Dfmin is the minimum value of the diameter of the mounting opening 8171;
dv is the inner diameter of the insert 81;
dm is the outer diameter of the main section 815 of the insert 81;
a is 1.1 to 1.6; and is
b is 1.0 to 1.5, wherein b Dv < a Dm.
According to an embodiment of the present invention, the maximum surface area of the inner surface F of the inner flange 817 may be defined by the following formula to obtain the maximum additional press-fit force generated by the flange 817 to improve the seal between the outer front surface of the flange 817 and the cylindrical body 821 of the fixing member 82:
where Fmax is the maximum surface area of the inner surface F of the inner flange 817;
dvmax is the maximum value of the inner diameter of the insert 81; and is
Dfmin is the minimum value of the diameter of the mounting opening 8171.
The piston rod 5 comprises an extension 51 coupling the additional piston 83 to the piston rod 5. According to an embodiment of the present invention, the additional piston 83 may include a seat 831, an opening (split) sealing ring 832, and a nut 833. The diameter of the open sealing ring 832 corresponds to the diameter of the inner chamber 813 of the insert 81. The nut 833 has a hexagonal surface which exerts a torque, so that the nut 833 can be fastened on the external thread of the threaded protrusion 511 of the piston rod extension 51 and thus serves to couple all components of the additional piston 83 to the piston rod 5. With the piston rod extension 51 coupled to the piston rod 5, the additional piston 83 may move axially along the central axis a together with the main piston 4. It will be appreciated that the outer diameter of the additional piston assembly 83 is smaller than the diameter of the main pipe 3, so that the working fluid is free to flow when the additional piston assembly 83 is located within the main pipe 3.
The open sealing ring 832 is loosely disposed over the seat 831 between the seat 831 and the nut 833 to define an annular channel extending between the seat 831 and a radially inner surface of the sealing ring 832. The sealing ring 832 provides a seal as the additional piston 83 moves within the inner chamber 813 of the insert 81 during both compression and rebound strokes.
It will be appreciated that the reduction of the outer diameter Dd of the end section 816 of the insert 81 increases the cross-sectional area of the axial annular channel 31 in the vicinity of the axial channel 825 of the fixing member 82, thereby greatly reducing or completely eliminating the flow restriction of the operating liquid to the foot valve 7 caused by the use of an insert 81 having a constant outer diameter. The greater the length Ld of the tip section 816 having the reduced diameter Dd, the greater the reduction in the flow restriction of the working liquid. However, the possible extension of the length Ld of the tip section 816 is limited by the required insert strength parameters and by the required geometry of the groove 814 (since the groove 814 extends not only along the entire main section 815 but also partially into the tip section 816 over the length Lg of the insert 81, with the bottom centerline of the groove 814 being inclined at an angle α relative to the central axis a of the hydraulic damper assembly 1). Thus, according to embodiments of the present invention, the length Ld of the tip segment 816 of the insert 81 may satisfy the following equation:
wherein L is the length of the insert 81;
lg is the length of the longest groove 814 of the plurality of grooves 814;
α is the angle of inclination of the bottom centerline of a groove of the plurality of grooves 814;
dv is the inner diameter of the insert 81;
dm is the outer diameter of the main section 815 of the insert 81;
dd is the outer diameter of the tip segment 816;
a is 1.1 to 1.6; and is
b is 1.0 to 1.5, wherein b Dv < a Dm.
Fig. 6a to 6f illustrate a manufacturing process of the insert 81 of the hydraulic compression stop 8. As best shown in fig. 6a to 6f, the manufacturing process is performed using two broaching dies 93, 94 in cooperation with a calibration mandrel 91. In an embodiment according to the invention, the calibration mandrel 91 has a narrowed end section 911 and a main section 912. The total length of the narrowed end section 911 is at least the desired height of the inner flange 817 of the insert 81. In addition, the diameter of the narrowed end section 911 of the calibration mandrel 91 corresponds to the desired diameter Df of the mounting opening 8171 of the inner flange 817. The narrowed end section 911 is gradually transformed into the main section 912, wherein the outer shape of the main section 912 corresponds to the desired inner shape of the inner chamber 813 of the insert 81. In other words, the main section 912 has a constant diameter that corresponds to the inner diameter Dv of the inner chamber 813 of the insert 81. On the outer surface of the main section 912, a plurality of bosses (protuberance)913 are formed thereon for forming a plurality of grooves 814 in the inner chamber 813 of the insert 81. The main section 912 of the alignment mandrel 91 terminates in a tapered section 914 for forming the tapered section 811 of the inner chamber 813 of the insert 81.
As best shown in fig. 6a, the first broaching die 93 has a generally cylindrical shape defining a circular broaching shaped hole. The diameter of the circular broach forming hole of the first broach die 93 corresponds to the desired reduced outer diameter Dd of the tip section 816 of the insert 81. As best shown in fig. 6d, the second broaching die 94 has a generally cylindrical shape defining a circular broaching shaped aperture. The diameter of the circular broach forming hole of the second broaching die 94 corresponds to the desired main outside diameter Dm of the main section 815 of the insert 81.
As best illustrated in fig. 6a, a preformed tube 81a (also referred to as a "blank") is first inserted over a cylindrical calibration mandrel 91. The preform tube 81a is supported by a ring 92 extending around a cylindrical calibration mandrel 91. According to an embodiment of the present invention, the preformed tube 81a may be made of steel (preferably with the following parameters: Rm ≧ 250MPa, Re ≧ 195MPa, A5 ≧ 35%). As best illustrated in fig. 6b and 6c, the first broaching die 93 is axially moved toward the ring 92 to press the preform tube 81a against the cylindrical calibration mandrel 91 for forming the tip section 816 having the reduced outer diameter. A flange 817 extends around the narrowed end section 911 of the cylindrical calibration mandrel 91 and the bottom of the inner housing 813, with the lower portion of the groove 814 located around the terminal portion of the main section 912 of the cylindrical calibration mandrel 91. During this first broaching operation, the percentage value of the maximum preform tube cross-sectional area reduction (also referred to as "cut edge") along the formed end section 816 having a reduced outer diameter is at most about 0.6. Additionally, it should be understood that the cut edge of the end section 816 may be at least 0.05 greater than the cut edge of the flange 817. As best illustrated in fig. 6d and 6e, the second broaching die 94 is used to form the main section 815 having a main outer diameter and the remainder of the inner chamber surface geometry, with the groove 814 and the remainder of the tapered section 811 being finally shaped to form the insert 81. Thus, after the second broaching operation, as represented in fig. 6f, the cylindrical calibration mandrel 91 is retracted through the ring 92, with the insert 81 resting on the ring 92.
The above embodiments of the present invention are merely exemplary. The drawings are not necessarily to scale and certain features may be exaggerated or minimized. These and other factors, however, should not be taken as limiting the spirit of the invention, the intended scope of which is indicated in the appended claims.
Claims (13)
1. A hydraulic damper assembly, said hydraulic damper assembly comprising:
a main tube extending along a central axis defining a fluid chamber for containing a working fluid;
an outer tube extending around the main tube defining a compensation chamber extending between the main tube and the outer tube;
a main piston located in the main tube dividing the fluid chamber into a compression chamber and a rebound chamber;
a piston rod extending into the main tube and coupled to the main piston for moving the main piston between a compression stroke and a rebound stroke;
a base valve in the compression chamber and coupled to the main pipe for controlling working fluid flow between the compression chamber and the compensation chamber; and
a hydraulic compression stop in the compression chamber for providing an additional damping force during the compression stroke;
the hydraulic compression stop including an additional piston coupled to the main piston for movement with the main piston between the compression stroke and the rebound stroke and an insert located in the compression chamber and coupled to the base valve;
the insert having a main section and a tip section, the tip section being located adjacent to the fixation member and the main section being in fluid communication with the tip section, the tip section having an outer diameter smaller than an outer diameter of the main section,
wherein the hydraulic compression stop comprises the securing member located between the main pipe and the foot valve for coupling the foot valve to the main pipe; and is
Wherein the insert is coupled to the fixation member via a press-fit engagement.
2. The hydraulic damper assembly of claim 1, wherein the insert and the stationary member are made of metal.
3. The hydraulic damper assembly as recited in claim 1, wherein the stationary member includes a head portion that extends outwardly from the stationary member and along the central axis toward the master piston,
the tip section of the insert includes an inner flange extending radially inward toward the central axis, the inner flange defining a mounting opening for receiving the head to establish the press-fit engagement.
4. The hydraulic damper assembly of claim 3, wherein a diameter of the mounting opening is smaller than a diameter of the head, a difference between the diameter of the mounting opening and the diameter of the head being in a range of 0.01mm to 0.5 mm.
5. The hydraulic damper assembly of claim 3, wherein the head has a tensile strength Rm greater than or equal to 300MPa, a yield strength Re greater than or equal to 250MPa, and a Rockwell B hardness of at least 51 HRB.
6. The hydraulic damper assembly of claim 3, wherein a height of the inner flange is greater than a height of the head, a ratio of the height of the inner flange to the height of the head being less than 2.
7. The hydraulic damper assembly of claim 3, wherein the mounting opening has a diameter that satisfies the following equation:
wherein Df is the diameter of the mounting opening;
dv is the inner diameter of the insert;
dm is the outer diameter of the main section of the insert;
a is 1.1 to 1.6; and is
b is 1.0 to 1.5, wherein b Dv < a Dm.
8. The hydraulic damper assembly of claim 3, wherein the mounting opening has a diameter that satisfies the following equation:
wherein Df is the diameter of the mounting opening;
dd is the outer diameter of the end segment;
dm is the outer diameter of the main section of the insert;
dv is the inner diameter of the insert;
a is 1.1 to 1.6; and is
b is 1.0 to 1.5, wherein b Dv < a Dm.
9. The hydraulic damper assembly of claim 3, said insert having an inner diameter that satisfies the following equation:
wherein Dv is the inner diameter of the insert;
dd is the outer diameter of the end segment;
dm is the outer diameter of the main section of the insert;
a is 1.1 to 1.6; and is
b is 1.0 to 1.5, wherein b Dv < a Dm.
10. The hydraulic damper assembly as recited in claim 3, wherein the insert defines a plurality of grooves that are circumferentially spaced from one another extending toward the base valve; and is
Wherein the length of the tip section of the insert satisfies the following equation:
wherein L is the length of the insert;
lg is a length of a longest groove of the plurality of grooves;
a is the inclination angle of the bottom center line of one of the grooves;
dv is the inner diameter of the insert;
dm is the outer diameter of the main section of the insert;
dd is the outer diameter of the end segment;
a is 1.1 to 1.6; and is
b is 1.0 to 1.5, wherein b Dv < a Dm.
11. The hydraulic damper assembly as recited in claim 1, wherein the fixed member defines a plurality of axial passages that are axially spaced from one another, extend through the fixed member, and are in fluid communication with the compression chamber, the base valve, and the compensation chamber.
12. The hydraulic damper assembly as recited in claim 1, wherein the stationary member defines a cavity in and in fluid communication with the compensation chamber, the cavity having an inner cylindrical surface for receiving the base valve.
13. The hydraulic damper assembly as recited in claim 12, wherein the foot valve is press fit against the inner cylindrical surface of the cavity.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010584792.7A CN111765194B (en) | 2020-06-24 | 2020-06-24 | Hydraulic damper assembly |
| US17/333,011 US11668367B2 (en) | 2020-06-24 | 2021-05-28 | Hydraulic damper assembly including a hydraulic compression stop |
| EP21179993.7A EP3933226A1 (en) | 2020-06-24 | 2021-06-17 | Hydraulic damper assembly including a hydraulic compression stop |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010584792.7A CN111765194B (en) | 2020-06-24 | 2020-06-24 | Hydraulic damper assembly |
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| Publication Number | Publication Date |
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| CN111765194A CN111765194A (en) | 2020-10-13 |
| CN111765194B true CN111765194B (en) | 2021-12-07 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202010584792.7A Active CN111765194B (en) | 2020-06-24 | 2020-06-24 | Hydraulic damper assembly |
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| US (1) | US11668367B2 (en) |
| CN (1) | CN111765194B (en) |
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| CN114645920B (en) * | 2020-12-21 | 2023-05-05 | 比亚迪股份有限公司 | Damper, shock absorber and car |
| CN113074207B (en) * | 2021-04-14 | 2022-04-29 | 北京京西重工有限公司 | Hydraulic damper |
| DE102021203895B4 (en) * | 2021-04-20 | 2024-11-14 | Zf Friedrichshafen Ag | Vibration damper with a hydraulic pressure stop |
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| CN114517819B (en) * | 2022-02-08 | 2023-07-25 | 北京京西重工有限公司 | Single tube damper assembly and hydraulic rebound stop assembly therefor |
| CN218408290U (en) * | 2022-09-23 | 2023-01-31 | 浙江路得坦摩汽车部件股份有限公司 | A hydraulic cylinder with linear change of tension and compression damping |
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|---|---|
| US20210404528A1 (en) | 2021-12-30 |
| US11668367B2 (en) | 2023-06-06 |
| CN111765194A (en) | 2020-10-13 |
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Denomination of invention: Hydraulic damper assembly Effective date of registration: 20230517 Granted publication date: 20211207 Pledgee: Jingxi Zhixing Zhangjiakou Automotive Electronics Co.,Ltd. Pledgor: BEIJINGWEST INDUSTRIES Co.,Ltd. Registration number: Y2023990000256 |
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Granted publication date: 20211207 Pledgee: Jingxi Zhixing Zhangjiakou Automotive Electronics Co.,Ltd. Pledgor: BEIJINGWEST INDUSTRIES Co.,Ltd. Registration number: Y2023990000256 |